EP0242741B1 - Disposition de garniture - Google Patents

Disposition de garniture Download PDF

Info

Publication number
EP0242741B1
EP0242741B1 EP87105356A EP87105356A EP0242741B1 EP 0242741 B1 EP0242741 B1 EP 0242741B1 EP 87105356 A EP87105356 A EP 87105356A EP 87105356 A EP87105356 A EP 87105356A EP 0242741 B1 EP0242741 B1 EP 0242741B1
Authority
EP
European Patent Office
Prior art keywords
sealing ring
sealing
ring
clamping
groove
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP87105356A
Other languages
German (de)
English (en)
Other versions
EP0242741A2 (fr
EP0242741A3 (en
Inventor
Theo Mack
Roy Edlund
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Busak and Luyken GmbH and Co
Original Assignee
Busak and Luyken GmbH and Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Busak and Luyken GmbH and Co filed Critical Busak and Luyken GmbH and Co
Publication of EP0242741A2 publication Critical patent/EP0242741A2/fr
Publication of EP0242741A3 publication Critical patent/EP0242741A3/de
Application granted granted Critical
Publication of EP0242741B1 publication Critical patent/EP0242741B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings

Definitions

  • the invention relates to a sealing arrangement with a sealing ring made of tough-elastic plastic inserted into the groove of two mutually movable machine parts and a clamping ring made of rubber-elastic material and placed between the sealing ring and the groove base, the axial expansion of which is considerably less than that of the sealing ring and the sealing ring axial position with respect to the sealing ring is fixed by stops such that the sealing ring is loaded in the region of an edge.
  • DE-A 2057 027 discloses a hydraulic seal with a cylindrical sealing ring and a rubber-elastic clamping ring which is arranged with its center over one end of the cylindrical sealing ring and therefore loads this end on one side.
  • the section of the clamping ring which projects beyond the sealing ring is supported on a preferably rigid support ring which does not have to perform any sealing tasks.
  • Proper functioning of this seal requires compliance with very tight tolerances with regard to the diameter of the sealing and support rings in relation to one another and also in relation to the diameter of the sealing surface, for example the diameter of a rod or shaft to be sealed.
  • a sealing arrangement is known from US Pat. No. 3,033,578, in which an essentially cylindrical sealing ring is loaded at its ends by an O-ring in each case.
  • the two O-rings assigned to the sealing ring are separated from one another by a web of the component receiving the sealing arrangement.
  • the two clamping rings are located centrally to annular sections of the sealing ring which bear against the sealing surface and are separated from one another by grooves.
  • Such a seal also requires close tolerances so that it ensures a usable seal for a reasonable period of time.
  • annular seal for sealing movable bodies which has a sealing ring which rests with three webs on a sliding surface to be sealed.
  • the sealing ring is arranged in a groove and is pressed against the sliding surface using a clamping ring.
  • the webs are arranged on the sealing ring in such a way that a central web serves as a seal and the two outer webs as guide webs prevent the seal from tilting.
  • the seal is suitable for high pressures. As the pressure increases, the middle bar is pressed against the sliding surface.
  • a hydropneumatic accumulator is known from DE-A 2 222 416, which has a sealing arrangement in the groove of a machine part, which seals the gap with respect to an adjacent machine part via a sealing ring.
  • the cross section of the sealing ring is biconcave and a clamping ring designed as an O-ring lies against the sealing ring.
  • the clamping ring is not fixed laterally in the groove and can shift.
  • the invention has for its object to form a sealing arrangement of the type mentioned so that it can be manufactured with greater tolerances than before and still ensures a good seal.
  • the sealing ring has an annular recess on its sealing surface which is in contact with the other machine part and the clamping ring is arranged approximately centrally to the recess.
  • the clamping ring in the sealing arrangement according to the invention therefore acts on the sealing ring in an area that lies between the locations with which the sealing ring is supported on the sealing surface.
  • the sealing ring can therefore bend to a greater or lesser extent without significantly influencing the contact pressure with which the sealing ring rests in the region of the edges on the sealing surface which delimit the portions of the sealing ring lying on both sides of the recess. It is therefore achieved by the sealing arrangement according to the invention a substantially constant contact pressure under operating conditions, which is maintained even when dimensional changes occur during operation of the sealing arrangement due to temperature fluctuations.
  • the surface sections adjoining the groove are conical in shape, so that in the relaxed state the sealing ring lies against the sealing surface with the edges lying on its outer end faces.
  • the conical surface sections increasingly contact the sealing surface of the other machine part, while at the same time increasing the pressure on the outermost edges. Both the increase in pressure on the outer edges and the increase in surface pressure in the area extending to the inner recess bring about an improvement in the sealing with increasing pressure.
  • the sealing ring can have ends at its ends projecting beyond the surface loaded by the clamping ring, with which the sealing ring abuts the bottom of the groove, so that these webs prevent evasion of the sealing ring and form abutments that lead to an Er contribute to increasing the contact pressure.
  • the pressure carrying capacity of the sealing arrangement according to the invention is thus further increased.
  • the clamping ring can be axially fixed in relation to the sealing ring in different ways. For example, it would be possible to insert support rings on both sides of the clamping ring into the groove receiving the clamping ring and the sealing ring. It would also be conceivable to provide the sealing ring with a recess on its side facing the clamping ring, which recess serves to receive the clamping ring. As a result, however, axial forces could be exerted on the sealing ring in an unfavorable manner on the sealing ring.
  • a preferred embodiment of the invention therefore provides that the groove receiving the sealing and clamping rings has a recess in the region of its center, into which the clamping ring engages. In this way it is ensured that the position of the clamping ring is correctly determined and only radially acting clamping forces are transmitted to the sealing ring, as are required for an optimal function of the sealing arrangement.
  • Fig. 1 shows the cross section of a sealing ring in the relaxed state.
  • This sealing ring 1 consists of a tough elastic plastic, for example based on PTFE or polyurethane. Its cylindrical base body is provided with a central recess 2 on one side. The limbs 3 delimiting the recess 2 have oblique end faces 4 which, with a concentric cylindrical surface 5 touching the ends of the limbs 3, form angles a opening inwards in the direction of the recess 2. On the other side, the sealing ring has two webs 6 at its ends.
  • the sealing ring 1 shown in FIG. 1 is installed together with a rubber-elastic clamping ring 11 in the groove 12 of one of two components 13, 14 to be sealed against one another and lies with the end faces 4 at the ends of its webs 3 on the sealing surface 15 of the other component 14.
  • the dimensions of the groove 12 are dimensioned such that the sealing ring 1 is received in this groove with little axial play and rests with its webs 6 on the bottom of the groove 12.
  • the rubber-elastic clamping ring 11 engages in a recess 16 which is provided in the region of the center of the groove 12.
  • the elastic rubber clamping ring 11 is a simple O-ring.
  • the diameter of the clamping ring 11 is smaller than the axial length of the recess 2 in the sealing ring 1, so that the clamping ring does not act against a rigid abutment, but on an area of the sealing ring in which there is no support for the sealing ring.
  • the sealing ring 1 suffers a deflection, as indicated in FIG. 2. This deflection can be so strong that the inclined surfaces 4 come to rest on the sealing surface 15 of the other component 14 at the ends of the legs 3, as is also indicated in FIG. 2.
  • the contact pressure with which the legs 3 rest with their end faces 4 on the sealing surface 15 is essentially determined by the clamping force of the clamping ring 11, which is largely independent of small differences in diameter.
  • This contact pressure is therefore largely independent of tolerances in the diameter of the other machine part 14 and also on the inside diameter of the recess 16 and the outside diameter of the sealing ring.
  • the sealing ring itself can easily adapt to different diameters of the other machine part 14, since its sections abutting the machine part 14 are radially flexible. Therefore, the sealing arrangement according to the invention is relatively insensitive to manufacturing tolerances. Its function is also not impaired by dimensional changes which can be attributed to temperature fluctuations, so that the seal according to the invention is also particularly suitable for those applications in which very strong temperature changes occur.
  • the sealing ring 1 When the sealing ring 1 is deformed, starting from the relaxed position shown in FIG. 1, based on the cross section of the ring, there is initially a tilting around the outer edges 7 of the sealing ring until the end faces 4 lie flat against the sealing face 15, as is the case with it shows Fig. 2. If the central section 1 were to bend further, there would be a tendency for the inner edges 8 to tilt, with the result that the sealing ring in the region of the outer edges 7 lifts off the sealing surface 15, which would be disadvantageous. In order to prevent such lifting, in the exemplary embodiment shown, the webs 6 are attached to the ends of the sealing ring 1, 3, which are supported on the bottom of the groove 12 and therefore prevent undesired deformations of the sealing ring 1, 3.
  • the angle a between the sealing surface and the sealing surface can vary approximately in the range from 0 ° to 15 ° .
  • the recess used to hold the tension ring could also be formed by filling a deeper groove on both sides of the tension ring with support rings.
  • a sealing arrangement according to the invention both on the circumference of a piston and in that for mounting and guiding a rod Nenden component can be arranged.
  • the seal according to the invention is also extremely suitable as a shaft seal. Finally it can be used to seal against any media. It is particularly suitable as a seal for both pneumatic and hydraulic systems.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Devices (AREA)
  • Sealing With Elastic Sealing Lips (AREA)

Claims (3)

1. Dispositif d'étanchéité comprenant une bague d'étanchéité (1, 3) en matière synthétique viscoélastique qui est insérée dans la rainure (12) de l'une de deux pièces de machine déplaçables l'une par rapport à l'autre, et un anneau de serrage (11) en matière élastique caoutchouteuse qui est agencée entre la bague d'étanchéité (1, 3) et un fond de rainure et sollicite radialement la bague d'étanchéité (1, 3) et dont l'extension axiale est beaucoup plus faible que celle de la bague d'étanchéité (1, 3) et dont la position axiale est fixée par rapport à la bague d'étanchéité (1, 3) par des butées de façon que la bague d'étanchéité (1, 3) soit sollicitée dans la zone d'un bord (7), caractérisé en ce que la bague d'étanchéité (1) présente un évidement annulaire (2) sur sa face d'étanchéité (5) adjacente à l'autre pièce de machine (14) et en ce que l'anneau de serrage (11) est agencé approximativement centralement par rapport à l'évidement, les sections de surface (4) contiguës à l'évidement (2) étant réalisées sous une forme conique de façon que la bague d'étanchéité (1, 3) soit, à l'état détendu, en appui sur la face d'étanchéité (5) par les bords (7) situés sur ses surfaces frontales extérieures.
2. Dispositif d'étanchéité suivant la revendication 1, caractérisé en ce que la bague d'étanchéité (1) présente à ses extrémités des ailes (6) qui débordent au-delà de la surface sollicitée par l'anneau de serrage (11) et par lesquelles la bague d'étanchéité (1) est en appui sur le fond de rainure.
3. Dispositif d'étanchéité suivant l'une des revendications précédentes, caractérisé en ce que la rainure (12), dans laquelle sont logés la bague d'étanchéité (1) et l'anneau de serrage (11), présente dans la zone de son milieu un renfoncement (16) dans lequel pénètre l'anneau de serrage (1).
EP87105356A 1986-04-24 1987-04-10 Disposition de garniture Expired - Lifetime EP0242741B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3613880 1986-04-24
DE3613880A DE3613880C1 (de) 1986-04-24 1986-04-24 Dichtungsanordnung

Publications (3)

Publication Number Publication Date
EP0242741A2 EP0242741A2 (fr) 1987-10-28
EP0242741A3 EP0242741A3 (en) 1988-05-25
EP0242741B1 true EP0242741B1 (fr) 1990-07-25

Family

ID=6299442

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87105356A Expired - Lifetime EP0242741B1 (fr) 1986-04-24 1987-04-10 Disposition de garniture

Country Status (5)

Country Link
US (1) US4714259A (fr)
EP (1) EP0242741B1 (fr)
JP (1) JPS62261762A (fr)
DE (1) DE3613880C1 (fr)
DK (1) DK205687A (fr)

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DK157947C (da) * 1987-03-20 1990-09-10 Shamban W S Europ Kombinationstaetning til taetning mellem to maskinelementer
DE3738988A1 (de) * 1987-11-17 1989-06-01 Busak & Luyken Gmbh & Co Dichtungsanordnung
DE3743726C1 (de) * 1987-12-23 1989-04-27 Busak & Luyken Gmbh & Co Dichtungsanordnung
US4889351A (en) * 1988-05-12 1989-12-26 Frost Stanley A Hydraulic seal
DE3821873A1 (de) * 1988-06-29 1990-02-08 Busak & Luyken Gmbh & Co Dichtungsanordnung
JPH02118177U (fr) * 1989-03-09 1990-09-21
US5083593A (en) * 1989-09-21 1992-01-28 Fogg Filler Co. Flip-flop seal
DE3940324A1 (de) * 1989-12-06 1991-06-13 Freudenberg Carl Fa Kolben- oder stangendichtung
DK675289D0 (da) * 1989-12-29 1989-12-29 Shamban W S Europ Taetningskonstruktion
DE4017036C2 (de) * 1990-05-26 1994-01-27 Busak & Luyken Gmbh & Co Dichtungsanordnung
US5253877A (en) * 1990-08-06 1993-10-19 Richard DeBiasse Piston ring having tapered outwardly extending wiper
CA2076912C (fr) * 1991-08-28 1999-05-04 Jerry F. Carlin Verin hydraulique avec bague d'usure amelioree
FR2688289B1 (fr) * 1992-03-06 1995-07-07 Leduc Rene Hydro Sa Joint tournant pour circuit hydraulique.
DE9315357U1 (de) * 1993-10-11 1995-02-16 Martin Merkel GmbH & Co KG, 21107 Hamburg Dichtungsanordnung
US5674055A (en) * 1994-05-16 1997-10-07 Pgi International, Ltd. Piston sealing arrangement for a sampling pump system
US5755446A (en) * 1996-12-24 1998-05-26 United Technologies Corporation Seal apparatus between a shaft and a non-linear inner surface of a housing
US6135008A (en) * 1998-03-16 2000-10-24 Haldex Brake Corporation Piston with lubricant-scraping ring and lubricant return ports
US6502826B1 (en) * 2000-10-30 2003-01-07 Caterpillar Inc Hydraulic cylinder piston seal
JP4587614B2 (ja) * 2001-08-01 2010-11-24 本田技研工業株式会社 ディスクブレーキ装置
DE10211366A1 (de) * 2002-03-14 2003-10-02 Hilti Ag Brennkraftbetriebenes Setzgerät
DE10356813A1 (de) * 2003-12-05 2005-07-07 Zf Transmission Technologies L.L.C., Batavia Gleitdichtung einer Kolben/Zylinder-Einheit
GB202001917D0 (en) * 2020-02-12 2020-03-25 Cross Mfg Company 1938 Limited Shaft mounting assembly

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8325499U1 (de) * 1984-01-26 A. Römheld GmbH & Co KG, 6312 Laubach Ringdichtung zum Abdichten von beweglichen Körpern
US28105A (en) * 1860-05-01 Peters
US2784013A (en) * 1953-12-21 1957-03-05 Bendix Aviat Corp Hydraulic seal
US3033578A (en) * 1959-08-10 1962-05-08 Gen Motors Corp Fluid seal
US3268235A (en) * 1965-03-29 1966-08-23 Alphonse A Jacobellis Piston accumulator seal
DE2057027C3 (de) * 1970-11-20 1974-04-25 Fichtel & Sachs Ag, 8720 Schweinfurt Hydraulisch beaufschlagte Dichtung
DE2222416C3 (de) * 1972-05-06 1975-07-03 Nabenfabrik Alfing Kessler Kg, 7083 Wasseralfingen Dichtungsanordnung für den Kolben eines hydropneumatischen Speichers
USRE28105E (en) 1972-09-22 1974-08-06 Sealing assembly
CH599487A5 (fr) * 1976-11-23 1978-05-31 Patent & Inventions Ltd
US4239242A (en) * 1978-12-18 1980-12-16 Burns William G Pipe union and seal
GB2096247B (en) * 1981-04-03 1985-02-20 Welding The Inst Sliding vacuum seal
US4566703A (en) * 1981-04-24 1986-01-28 Microdot Incorporated Seal assembly
FR2525313A1 (fr) * 1982-04-19 1983-10-21 Joint Francais Joint d'etancheite en elastomere
US4496161A (en) * 1982-10-25 1985-01-29 The Gates Rubber Company Radially extensible joint packing with O-ring

Also Published As

Publication number Publication date
US4714259A (en) 1987-12-22
EP0242741A2 (fr) 1987-10-28
DK205687D0 (da) 1987-04-23
EP0242741A3 (en) 1988-05-25
JPS62261762A (ja) 1987-11-13
DE3613880C1 (de) 1987-07-02
DK205687A (da) 1987-10-25

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